Machine for forming curved surfaces on heels and the like



April 6, 1937. a. T. GIALDINI MACHINE FOR FORMING CURVED SURFACES ON HEELS AND THE LIKE Filed July 14, 1951 7 Sheets-Sheei 1 3144);: wtoc 15! ram/01m;

elbtozmqa B. T. GIALDINI April 6, 1937.

MACHINE FOR FORMING CURVED SURFACES ON HEELS AND THE LIKE Filed July 14, 1951 -'7 Sheets- Sheet 2 gnoemto'r,

B. Z 6701a;

7 Sheets-Sheet 3' April 6, 1937. B. T GlALDlNI MACHINE FOR FORMING CURVED SURFACES ON HEELS AND THE LIKE Filed July 14, 1951 April 1937- B. T. GIALDINI $076,123

MACHINE FOR FORMING CURVED SURFACES ON HEELS AND THE LIKE Filed July 14, 1931 7 Sheets-Sheet 4 April 1937. B.- T. GIALDINI 2,076,123

MACHINE FOR FORMING CURVED SURFACES ON HEELSAND THE LIKE Filed July 14, 1931 7 Sheets-Sheet 5 I 4 2 5a m /58 154a 5 a 9 jig 9a I 57 E I' l 150 g 78 I20 70 66 April 1937- B. T. GIALDINI 2,076,123

MACHINE FOR FORMING CURVED SURFACES ON HEELS AND THE LIKE Filed July 14, 1931 '7 Sheets-Sheet 6 gwue'ntoz B 1 6221107121 April 6, 1937. 3,1. GIALDlNl I 7 MACHINE FOR FORMING CURVED SURFACES ON .HEEL S AND THE L IKE Filed Jill 14,-.1931 7 Shee'cLs-Sheet 7 gwventoc Patented Apr. 6, 1937 UNITED STATES PATENT OFFICE MACHINE FOR FORMING CURVED SUR- FACES ON HEELS THE LIKE 13 Claims.

My invention relates to machines for forming curved or variably curved surfaces on articles such as heels for womens shoes.

Such a heel is usually formed from wood, and

may be finished by the application of leather to its surfaces, and usually includes a surface facing forwardly in the shoe, and extending downwardly from the sole at the rear of the instep.

The forward or front surface of a heel is usually formed in a block of wood by a milling operation.

The usual heel also includes a rearwardly facing variably curved surface which extends from one curved side edge of the front surface to the other curved side edge thereof.

In all methods of making such heels, the rearwardly facing variably curved surface is formed by one or more cutter blades having a particular curve, the cutter blade or blades rotating about an axis and operating on a heel block which is simultaneously rotated about an axis parallel with the axis of rotation of the cutter blade, moved longitudinally in the direction of the axis of rotation, tilted with respect to the axis of rotation, and the distance of the axis of rotation of the block from the axis of rotation of the cutter blade being varied during the other three simultaneous movements of the block.

In thus forming the rear surface of such a heel, it is sometimes customary to mount the heel block in a jack or fixture provided with manual control means, and to form first one half, and then the other half of the rear heel surface by successively rotating opposite sides of the block in contact with a rotary forming cutter, at the same time varying the angle, varying the elevation of the block with respect to the cutter, and varying the distance of the axis of rotation of the block from the axis of rotation of the cutter.

Two laterally spaced rotary forming cutters 0 are frequently employed, using one cutter for forming one side of the rear surface of the heel and the other cutter for forming the other side, and the jack or fixture in such case is arranged to be moved manually from one cutter to the other.

A tilting track is usually located adjacent each cutter and cooperates with a follower on the jack or fixture for angling or tilting the block, and similarly an elevating track is located adjacent each cutter and cooperates with a follower on the jack or fixture for elevating the block, while a contour cam and follower are provided for varying the distance of the axis of rotation of the block from the axis of rotation of the cutter during .515 each cutting action whereby the resultant heel has the desired contour with respect to a normally horizontal plane.

In such usual machines for forming heels as aforesaid, the several movements of the jack are attained by manual operation, and the spindles for the cutters are located below the cutter knives, whereby it is practically impossible in such a machine to obtain automatic operation thereof by reason of the interference which would occur between the control mechanisms and the spindle driving mechanisms.

On the other hand, there has been proposed a machine for automatically forming heels which includes two rotary cutters, an endless conveyer with four jacks, and cam means adjacent each cutter for properly moving a block being partially formed by the cutter.

In such a machine the operator loads one jack while blocks in two of the other jacks are each being partially formed by the adjacent cutter, each cutter forming substantially one-half of the rear heel surface.

The fourth jack is located opposite the loading jack and between the cutters, and the partially formed block therein is idle during any particular cutting action of the cutters.

The operator has only suflicient time to load the loading jack during any particular cutting action, and consequently the operator can only operate one machine at a time.

Each of such automatic machines including four jacks is only capable of turning out one particular style of heel with one particular set up of the cutter knives and the cams therefor.

On the other hand in the usual heel factory the demand is for relatively short runs of a plurality of different styles of heels, rather than for a long run of a single style of heels, and the foregoing proposed automatic machines are not economical for meeting this demand, because each of such machines requires the undividedattention of an operator for keeping its four jacks continuously loaded.

The objects of the present invention include the a control mechanisms for the machine may be located below the cutters and will not interfere therewith.

Further objects of the invention include the provision of an automatic machine for automatically forming the rear surfaces of heels and the like, the machine including a single jack, whereby a single operator may tend a plurality of the machines, each machine turning out a different style of heel.

The foregoing and other objects are attained by the apparatus, parts, improvements, and combinations, which comprise the present invention, and which are particularly and distinctly pointed out and set forth in the appended claims forming part hereof.

In general terms the improved machine of the present invention includes means for removing surface material from one side of a heel block by moving the heel block relative to one cutter from one exactly predetermined locus at one side of the axis of the heel block to a second locus thereon, means for moving the heel block from the first cutter to another cutter, and means for simultaneously rotating the heel block during movement thereof from the first cutter to the second cutter so as to contact the heel block with the second cutter at a third exactly predetermined locus on the heel block preferably symmetrically opposite the first locus.

Preferred embodiments of the improved machine are illustrated in the accompanying drawings forming part hereof, in which Figure 1 is a side elevation of the improved machine, the parts thereof being in their relative positions just after loading the jack of the machine;

Fig. 2, a front elevation thereof;

Fig. 3, a top plan view thereof;

Fig. 4, an enlarged fragmentary view similar to Fig. 2, illustrating details of the jack, and other parts of the machine;

Fig. 5, a fragmentary sectional view looking in the direction of the arrows 55, Fig. 4, and illustrating the operation of one of the electric control switches for the machine, after forming one side of the rear surface of the heel block;

Fig. 6, an enlarged fragmentary sectional view as on lines 6-6, Figs. 2, 3, and 4;

Fig. '7, a fragmentary transverse sectional view as on line 'l-'l, Fig. 6, illustrating the reversing drive mechanism for the machine;

Fig. 8, a fragmentary horizontal sectional view of the machine, with distant parts removed as on line 88, Fig. 6;

Fig. 9, a similar view as on line 99, Fig. 6;

Fig. 10, a similar view as on line Ill-ID, Fig. 6;

Fig. 11, a similar view as on line I ll i, Fig. 6;

Fig. 12, an enlarged fragmentary plan view illustrating the relative positions of the several parts of the machine at the beginning of the first cutting operation on a block by one of the cutters;

Fig. 13, a similar view illustrating the relative positions of the parts at the end of the first cutting operation;

Fig. 14, a similar view illustrating the relative positions of the parts at the beginning of the second cutting operation by the other cutter;

Fig. 15, a similar view illustrating the relative positions of the parts at the end of the second or final cutting operation;

Fig. 16, a diagrammatic view illustrating one form of wiring for the electrical parts of the machine, and their relationship with each other and with the mechanical parts; and

Fig. 17, a top plan view illustrating an arrangement of four of the machines, adapted for being operated by a single operator, and each machine being adapted for turning out a separate style of heel.

Similar numerals refer throughout the several views.

One embodiment of the improved machine or apparatus for forming curved surfaces on heels and the like is illustrated in Figs. 1 to 16 inclusive and is indicated generally at l, and includes a base frame 2 which is supported on legs 3a, 3b, 3c, and 3d, and a cutter mounting bracket 4 is secured to and extends upwardly from the base frame 2.

The bracket 4 is provided with a front face 4 on the upper end of which is secured laterally spaced cutter mechanisms indicated generally by 5a and 5b, in Figs. 1 to 4 inclusive, 6, and 12 to 15 inclusive.

As illustrated in Figs. 1, 2, 4, and 6, the cutter mechanism 5a includes a separate drive motor 6a having a rotor shaft la whose axis of rotation is normally vertical and which extends below the lower end of the motor 6a, and a cutter 8a is secured to the lower end of the rotor shaft la, and the cutter 8a includes a plurality of vertically and radially extending cutter blades 90. each having a curved cutting edge 9a of the desired contour for forming the desired heel surface, as best shown in Fig. 6.

Similarly as illustrated in Figs. 1, 2, and 4 the cutter mechanism 5?) includes a separate drive motor 65 having a rotor shaft 11) whose axis of rotation is normally vertical and which extends below the lower end of the motor 65, and a cutter 8b is secured to the lower end of the rotor shaft 15, and the cutter includes a plurality of vertically and radially extending cutter blades each having a curved cutting edge 91) of the desired contour for forming the desired heel surface, the cutting edges 9a and 9b, ,usually having identical contours.

The forming machine I further includes means for releasably mounting a block B to be formed, such as the improved jack or fixture indicated generally by ID, as best shown in Figs. 2 and 4, and automatic means indicated generally by H, as best shown in Figs. 1, 6, and 8, for imparting oscillatory movement to the jack between and to and from the cutters are operatively mounted on the base frame 2 below the cutters 8a and 8b and their blades 9a and 9b.

From a different standpoint, the means I l and the parts associated therewith as hereinafter set forth in greater detail, comprise drive means operatively associated with the block mounting means [0 for imparting oscillatory movement to the block mounting means back and forth between the cutters.

The forming machine I furthermore includes means indicated by l2, and best shown in Figs. 1, 6, and 9 arranged for rotating the jack in and the heel block 13 mounted therein about the normally vertical axis Y during movement thereof on the jack moving means I I from either cutter to the other, and for further rotation of the jack l0 and heel block B about the axis Y, after the jack I0 has been moved by the jack moving means H to a cutting position with respect to either cutter, whereby each cutter may form substantially one-half of a rear heel surface on to similar parts the block B, as well shown in Figs. 12 to 15 inclusive.

The machine I furthermore includes jack tilting means indicated generally by I3 and best shown in Fig. l, for varying the angle of the jack l0 and block B mounted therein, with respect to the operating cutter during each successive cutting action, and jack elevating means indicated generally by M and best shown in Fig. 4, for elevating the jack H! and block B during each successive cutting action.

Both the jack tilting means l3 and the jack elevating means l4 are operatively mounted on the jack moving means I l, in a novel manner as will hereinafter be set forth in greater detail.

The jack moving means H, the jack rotating means 12, the jack tilting means [3, and the jack elevating means M, are associated with each other by novel means hereinafter set forth in detail for proper automatic operation to automatically form a rear surface on the heel block B, after loading of the block B in the jack l8, and the several means II, l2, l3, and 14, each providing a different movement for the jack I0 and the block B mounted therein, are all driven by a common drive shaft 15 shown in Figs. 1, 6, and '7 and the drive shaft I5 may receive power from any suitable source as by means of a belt and pulley connection indicated generally by IS with a drive motor i1 secured upon the base frame 2 at the rear end thereof.

The common drive shaft I5 is journalled in the frame 2, and reversing gearing indicated generally by l8 and shown in Figs. 6 and '7, is operatively mounted in the frame 2, and provides a reversing drive Connection between the drive shaft 15, which as illustrated is horizontal, and a first intermediate shaft l6, which as illustrated is vertical, and is journalled in the frame 2.

The reversing gearing i8 may be of any desired arrangement, and as illustrated in Figs. 6 and '7 includes bevel pinions 26a and 26b journalled on the shaft l5 on opposite sides of the lower end of the first intermediate shaft l9, which terminates above the shaft l5.

A bevel drive gear 23 is secured upon the lower end of the first intermediate shaft l9 and is meshed with both of the opposite bevel pinions 26a and 261).

A clutch cone 22a is secured to the bevel pinion 26a and extends towards an opposite clutch cone 221) which is secured to the bevel pinion 20b and extends towards the opposite clutch cone 22a.

A clutch engaging member 23 is slidably keyed on the shaft 55 between the cones 22a and 22b, and the external conical surfaces 24a and 241) respectively of the cones 22a and 22b taper towards each other, and are located respectively within internal conical -surfaces 25a and 25b formed respectively in opposite ends of the clutch engaging member 23.

Reversing clutch actuating generally by 26 and shown in Figs. 1, 6, 7, and 16, are provided and operatively associated with the jack moving means II and the jack rotating means 12 for properly reversing the first intermediate shaft !6 by proper movement of the clutch engaging member 23 to successively engage the cones 22a and 22b by sliding the clutch engaging member 23 towards one of the cones 22a and 2219 so that the inner conical surface 25a or 251) of the clutch engaging member 23 grips the outer conical surface 24a or 241) of the cone 22a or 221), as the case may be.

As illustrated in Figs. 6, 7, and 16, the reversing means indicated as by means of a cap screw clutch actuating means 26 is electrically operated, and includes a slide shaft 21 parallel with the drive shaft l5, and the shaft 21 is slidably mounted in the frame 2 below the shaft l5.

An armature 28 is secured on the central portion of the slide shaft 21, and a finger 29 extends upwardly from the armature 28 into an outwardly opening annular groove 30 formed in the central portion of the clutch engaging member 23.

A set of electro-magnets 29a are mounted on the frame 2 at one side of the armature 28, and another set of electro-magnets 291) are mounted on the frame 2 at the other side of the armature 26.

Each set of electro-magnets is successively energized by operation of the machine as hereinafter set forth in detail, and accordingly the armature 28 is successively moved and maintained adjacent the inner ends of the energized set of magnets, whereby the clutch engaging member 23 willbe successively moved for engagement alternately with the cones 22a and 22b, thereby successively reversing the direction of rotation of the first intermediate shaft IS.

The forming machine I may furthermore include as illustrated in Fig. 6, a second intermediate shaft SI, and a third intermediate shaft 32.

A pinion 33 is secured on the first intermediate shaft 19 and meshes with a gear 34 secured on the second intermediate shaft 3|, and a pinion 35 is secured on the second intermediate shaft 3! and meshes with a gear 36 secured on the third intermediate shaft 32.

Accordingly the third intermediate shaft 32 is alternately rotated in reverse directions by the just described gearing connection with the first intermediate shaft 19.

The jack in includes a movable base 31 which may be termed a movable block positioning member which is pivotally secured at one 'end as by means of a pivot pin 38 upon the upper end of a jack elevating and rotating shaft 39, as best shown in Figs. 2 and 4.

The jack elevating and rotating shaft 39 extends normally vertically through and fits in a drive sleeve 46, and the elevating and rotating shaft 36 is slidably secured to rotate with the drive sleeve 46 as by means of a key 4! seated in the shaft 39 and sliding in a longitudinally extending keyway 42 formed in the inner cylindric surface of the drive sleeve 46, as shown in Fig. 6.

The drive sleeve 49 preferably extends through a normally vertically extending chamber 43 formed in the outer end 44 of a swinging arm 45 which comprises part of the jack moving or swing- 4 ing means II, and the sleeve 40 is journalled in the bore 43 of the arm 45, as by means of a set of upper and lower bearings 46-! and 46- 2, which are preferably anti-friction bearings, as illustrated in Figs. 4 and 6.

The inner end of the swinging arm if: has formed therein a normally vertically extending bore 41, and a pivot shaft 48 extends through and fits in the bore 41 and is secured to the arm. 45 as by means of a pin 49, as shown in Fig. 6.

The pivot shaft 48 extends normally vertically and is suitably journalled in the frame 2.

In addition to the swinging arm 45 thus pivotally mounted in the frame 2, the jack moving or swinging means I! includes a swinging gear 50, best shown in Figs. 5, 6, .and 8 coaxial with the pivot shaft 48, and secured to the arm 45, 5| extending through a bore formed in the swinging gear 58and screwed into a suitable threaded aperture the arm 45. I

The swinging gear 59 is meshed with a swinging pinion 53 which is co-axial with the third intermediate shaft 32.

The shaft 32 extends through the swinging pinion 53 and preferably adjustable frictional clutch means indicated generally by 54 and shown in Fig. 6, are interposed between the swinging pinion 53 and the third intermediate shaft 32, thereby providing a releasing frictional driving connection between the shaft 32 and the swinging pinion 53.

As illustrated in Fig. 6, the releasing frictional clutch means 54 is of the disk type of clutch, and includes a drum member 55 to one end of which the swinging pinion 53 is secured, as by means of a cap screw 58, and the clutch drum member 55 is rotatably mounted on the third intermediate shaft 32.

The clutch means 54 furthermore include a sleeve 51 secured to the third intermediate shaft 32, as by key means 58.

One set of friction disk plates 59 is slidably keyed to the sleeve 51, and another set of friction disk plates 59' is slidably keyed to the drum 55, the plates of one set being interposed between the plates of another set in a usual manner.

One outer plate of the interposed sets of plates abuts against a shoulder flange 69 formed on the sleeve 5?, and a compression spring 6| is interposed between the other outer plate of the interposed sets of plates and an adjusting nut 62 which is screw mounted on the sleeve 57, whereby a variable pressure may be applied between the sets of friction plates, and in consequence of which a releasable swinging connection is provided between the third intermediate shaft 32, through the clutch means 54, the swinging pinion 53, and the swinging gear 59, with the arm 55.

Accordingly, the arm 45 will be swung by rotation of the third intermediate shaft 32, until the arm 65 encounters a resisting torque which is greater than the frictional swinging torque applied through the clutch means 54, in which case the arm 45 will not swing further, but the third intermediate shaft 32 will continue its rotation for the purposes hereinafter to be set forth.

In other words the jack moving or swinging means i l includes the swinging arm 45, on which the jack l [i is operatively mounted, the reversible rotatable third intermediate shaft 32 and releasing frictional driving means between the shaft 32 and the arm 45, comprising the clutch means 54, the swinging pinion 53 secured to the releasable drum 55 of the drum clutch means 54 and the swinging gear 59 secured to the arm 45 and meshed with the swinging pinion 53.

The jack rotating means indicated generally by l2 and best shown in Figs. 1, 6, and 9, as aforesaid, comprises an epicyclic gear train including a jack rotating drive gear 63 secured to the third intermediate shaft 32, as by means of a pin 54, and the drive gear 63 is meshed with a jack rotating idler gear 65 which is journalled on the pivot shaft 58, and the idler gear 65 is meshed with a jack rotating driven gear 65 which is secured to the lower end of the jack drive sleeve 40 as by key means 61.

Accordingly rotation of the shaft 32 serves to rotate the jack during swinging of the arm 45, as well as when the arm 45 comes to rest, and as the result of which the jack H3 is rotated during swinging of the arm 45 so that the proper locus on each side of a block B mounted in the 52 formed in jack [9 is brought into the proper position for proper cutting action by each of the cutters.

The jack tilting means indicated generally by l3 and best shown in Fig. 4, includes a link bar 68 which is pivotally connected at its upper end as by pin 69 with the base 3'! of the jack [9.

The axis of the pin 69 is parallel with the axis of the pin 38, which, as aforesaid pivotally secures one end of the base 31 upon the upper end of the jack elevating and rotating shaft 39.

The link bar 68 extends downwardly from the pivot pin 69 to a position below the swinging arm 45, where the lower end of the link bar 68 is pivotally connected as by a pivot pin '19 with the outer end of a raising and lowering arm ll The inner end of the arm '35 is secured to the lower end of a piston shaft 72 which is slidably mounted in a bore 13 formed in the lower end of the jack elevating and rotating shaft 39, there being a longitudinally extending slot the tubular wall 75 of the lower counterbored portion of the shaft 39, and the arm H extends through the slot or opening 74.

A tilting cam follower roller 76 is rotatably mounted at the lower outer corner of the arm II, and the axis of rotation of the roller 76 is perpendicular to the axis Y of the shaft 39 about which the jack H3 is rotated, and which coincides with the longitudinal axis of the shaft 39.

It is evident that raising and lowering of the arm ll a greater distance than any simultaneous raising and lowering of the jack elevating and rotating shaft 39 will tilt the jack base 31 upwards about the pivot pin 38.

For the purpose of raising and lowering the arm H, a tilting cam '1? is provided, and as best shown in Figs. 4, 6 and 10 the tilting cam 11 includes a semicircular track 73 whose axis coincides with the axis Y, and the successive points on the track 78 have different displacements from any reference plane perpendicular to the axis Y, the high point 19 of the track 18 being located on the outer side of the axis Y, and being maintained in such position by means which will be hereinafter described in detail.

From the high point '19 the track 78 slopes equal distances to two diametrically opposite low points 89a and 80b, and the portion of the tilting track 73 between the low point 86a and the high point 79, by rolling thereover of the roller 76, 8

causes elevation of the arm H with a consequent tilting of the jack 19, during cutting of one side of the heel block 13, and the portion of the track 18 between the other low point 891) and the high point 79 functions similarly during cutting of the other side of the heel block.

The jack elevating means It and best shown in Fig. 4, as aforesaid includes the heretofore described jack elevating and drive shaft 39, and an elevating arm 8! is secured at its inner end to the lower end of the elevating and drive shaft 39, and an elevating cam follower roller 82 is rotatably mounted on the outer end of the elevating arm 8!, and the axis of rotation of the roller 82 is perpendicular to the axis Y.

Raising and lowering of the arm 8i secured at the lower end of the jack elevating and drive shaft 39 obviously raises and lowers the jack I0, whose base 3'! is secured at the upper end of the shaft 39, as aforesaid.

For the purpose of thus raising and lowering the arm 8i, an elevating cam 83 is provided, and the elevating cam 83 includes a semi-circular track 34 whose axis coincides with the axis Y, and the successive points on the track 84 have I4 formed at one side in different displacements from any reference plane perpendicular to the axis Y, the high point 85 of the track 84 being located'on the inner side of the axis Y at a position diametrically opposite the high point 19 of the track 18 of the tilting cam 11.

From the high point 85, the track 84 slopes equal distances to two diametrically opposite low points 86a and 86b, and the portion of the elevating track 34 between the low point 860. and the high point 85, by rolling thereover of the roller 82, causes elevation of the shaft 39 and of the jack I0 secured at its upper end, during cutting of one side of a heel block B, and the portion of the track 84 between the other low point 86b and the high point 85 functions similarly during cutting of the other side of the heel block.

One of the novel features of the present invention includes operatively mounting the coaxial tilting cam 11 and elevating cam 83 for swinging movement with the swinging arm 45, and at the same time maintaining the vertical plane T, Figs. 10, 11, and 12 to 15 inclusive, passing through the diametrically opposite high points 19 and 85 of the tilting and elevating cams constantly perpendicular with the vertical plane U, Figs. 3, 6, and 12 to 15 inclusive, passing through the parallel vertical axes of rotation of the cutters 8a and 81).

Means for thus moving the cams 11 and 83, and maintaining their relative positions, includes a cam mounting arm 81 shown in Figs. 1 and 6, the inner end of which has formed therein a normally vertically extending bore 88 which fits on the lower end of the pivot shaft 48 below the frame 2, and the-cam mounting arm 81 is secured to the shaft 58 as by means of pins 89.

The outer end of the cam mounting arm 81 has formed therein a normally vertically extending tubular chamber 90 in which a normally vertically extending cam rotating and adjustable mounting sleeve 9I is journalled preferably by means of upper and lower anti-friction bearings 92I and 922 as shown in Fig. 6.

The upper end 93I of the sleeve 9| extends above the arm 81, and the lower end 93--2 of the sleeve 9! extends below the arm 81, and is threaded for purposes hereinafter to be set forth.

A telescoping cam supporting sleeve 94 is slidably located within the bore of the mounting sleeve 9i and the upper end 95-4 of the telescoping sleeve extends above the upper end 93I of the mounting sleeve 9|, and the upper end 95I' of the telescoping sleeve 94 is secured to and mounts the disk bottom wall 96 of an elevating cam seating cup 91.

The cup 91 furthermore includes a tubular wall 98 extending upwardly from the disk bottom wall 96, and the upper peripheral face 99 of the tubular wall 98 is in the form of a seat in which the tilting cam 11 is located and mounted, as shown in Fig. 6.

Within the bore of the telescoping sleeve 94, a telescoping cam supporting shaft I00 is slidably located, and the upper end IOII of the sup porting shaft extends above the upper face of the disk bottom wall 96 of the cup 91, and a circular disk plate I92 is secured upon the upper end lfil-I of the supporting shaft I00.

The elevating cam 83 is seated and mounted on the upper face of the disk plate I02, as shown in Fig. 6.

The lower end 932 of the sleeve 9i has formed therein diametrically opposite longitudinally ex-, tending slots I03, and the lower end IOI--2 of the supporting shaft I00 has formed therein a longitudinally extending slot I04. A pin I05 is secured in the telescoping sleeve 94 and extends through the slots I03 and. I04 whichare alined with each other, and a nut I06 is screwed on the threaded lower end 93-2 of the sleeve 9|, and the outer extremities of the pin I05 extend over and are supported on the upper face of the nut I66, whereby the elevation of the tilting cam 11 supported on the telescoping sleeve 94 may be varied by screwing up or down the nut I06.

Similar means are provided for varying the elevation of the elevating cam 83, there being formed diametrically opposite longitudinally extending notches I01 in the lower end 932 of the sleeve 9i, the notches 101 being spaced 90 degrees from the slots, I03.

Similar notches are formed in the telescoping sleeve 94, and a pin I08 is secured in the lower end IOI-2 of the shaft I00, and the extremities of the pin I08 extend through the notches and are seated on the upper face of a nut I09, which is screwed on the threaded lower end 93-2- of the sleeve 9| below the nut I06.

Means indicated generally by H0 and best shown in Figs. 6 and-11 are provided for maintaining the vertical plane T, Figs. l0, l1, and 12 to 15 inclusive, including the high points 19 and 85 of the cams 11 and 83, at right angles with the vertical plane U, Figs. 3, 6, and 12 to 15 inclusive, extending through the axes of the cutters 8a and 8b, as aforesaid.

The cam positioning means IIO, as shown in Figs. 6 and 11, comprises an epicyclic gear train including a gear I I I mounted on the lower end of the pivot shaft 48 between the arm 81 and the bottom of the frame 2. The gear III is secured against rotary movement as by means of a cap screw II2 extending through the gear and screwed into the bottom of the frame 2.

An idler pinion I I 3 is meshed with the gear I I2 and is pivotally mounted on the upper face of'the arm 81, and the pinion H3 is meshed with a swinging and rotating gear II4 which is secured to the upper end 93--I of the cam rotating and mounting sleeve 9|.

Accordingly by reason of the fixing of the gear I I I against rotation, swinging of the arm 81 with the pivot shaft 48 and the arm 45, causes rotation of the cams about the axis Y so as to maintain the plane T constantly at right angles to the plane U, as is necessary in order to carry out the desired mode of operation of the machine I.

In addition to the base or movable block positioning member 31, the jack I0 includes releasable clamping means indicated generally by I20 and best shown in Figs. 2 and 4, by which the block B may be releasably clamped on the base or movable block positioning member 31' at the end thereof which is pivotally secured to the jack shaft 39.

For varying the distance of the axis of rotation Y of the jack and block from the axis of rotation of either cutter during rotation of the jack and block in a cutting operation, a contour cam I39 is secured on the shaft 39 below the jack base 31, as best shown in Figs. 4, 5, and 12 to 15 inclusive.

The contour cam is in the form of a normally horizontal disk whose outer periphery I3I is generally of the U shape and symmetrical with respeot to an axis X indicated in Figs. 12 to 15 inclusive lying in the upper surface of the disk cam I30, the axis X being'perpendicular to the axis Y.

The base portion I33 of the U periphery I3I of the disk contour cam I 30 is located between the jack rotating shaft 39 and the pivot shaft 48.

A contour cam guide wheel supporting arm I34a is pivotally mounted at one end on the upper end of the pivot shaft 48, and is pivotally connected at its other end with one end of an adjustable positioning link I35a, and the other end iof the adjustable link I35a is adjustably connected as by means of screw and nut means I360 with a bracket I3Ia pivotally mounted on the frame 2, as best shown in Figs. 2, 3, 4, and 12 to 15 inelusive.

A contour cam guide wheel I30a is operatively mounted for rotation about a normally vertical axis on the supporting arm I34a, when contacting with the periphery of the disk cam I30, as shown in Figs. 14 and 15.

Similarly a contour cam guide wheel supporting arm [34?) is pivotally mounted at one end on the upper end of the pivot shaft 48, and is pivotally connected at its other end with one end of an adjustable positioning link I351), and the other end of the adjustable link I351) is adjustably connected as by means of screw and nut means I361 with a bracket I3'Ib pivotally mounted on the frame 2.

A contour cam guide Wheel I381) is operatively mounted for rotation about a normally vertical axis on the supporting arm I341] when contacting with the periphery of the disk cam I30, as shown in Figs. 12 and 13.

The wheel I38a is located below the cutter 3a and the wheel I382) is located below the cutter 81).

Operation of the machine as hereinafter set forth in detail, serves to rotate one side of the periphery I3I of the contour cam I30 against the cam guide wheel I38a during cutting operation of the cutter 8a, and by reason of the U shape of the periphery I3I of the rotating contour cam, the distance between the axis of rotation Y of the jack and block and the axis of rotation of the cutter 8a is varied during rotation of the contour cam I30. Similarly, when the cutter 0b is operating, the other side of the periphery I3! of the contour cam I30 rotates against the cam guide wheel I382).

For successively energizing the sets of electromagnets 29a and 29b to successively reverse the direction of rotation of the first intermediate shaft i9, and consequently of the third intermediate shaft 22, means are provided which may include an electric power supply line indicated generally by M0 in Fig. 16, a two circuit selector switch I4I interposed between the power supply line I40 and the sets of electro-magnets 29a and 29b, and preferably electro-magnetic selector switch actuating means indicated generally by I4Ia and hill); for successively actuating the switch I4! to conmeet the power supply line I40 first with one and then the other set of electro-magnets 29a and 29b.

The power supply line as illustrated includes conductors Mil-I and I40-2, and the selector switch I4I includes a conductor bar I4I-I which is pivotally mounted at its central portion as by pin I42I, and is connected as by a conductor I43I with the power conductor I40-I.

The switch II also includes a conductor bar I4I-2 which is pivotally mounted at its central portion as by pin I42-2, and is connected as by a conductor I43-2 with the power conductor I402.

The pivot pins I42I and I422 are alined With each other so that the conductor bars I4 II and I4I2 may pivot or swing with each other, and at one side of the pivot pins, the conductor bars I4I--I and I4I-2 include respectively arms I4IIa and arms I4I2a, and at the other side the conductor bars include respectively arms I4I-Iband I4I-2b.

The arm I4IIa\ is preferably angled with respect to the arm I4IIb; and the arm I4I-2a is similarly angled with respect to the arm II-2b.

For swinging the conductor bars together, a non-conducting link MM is pivotally connected at one end with the arm I4Ila and at the other end with the arm I4 IEa, and a non-conducting link I441), extending parallel with the link I44a, may be pivotally connected at one end with the arm I4I-Ib and at the other end with the arm I4I-2b The outer ends of the arms 54 II a and I4 I-fla are arranged for movement into electrical connection respectively with contacts Hid-4a and I452a; and the contact I45Ia is connected by a conductor I40-Ia. with one terminal HIT-Ia of the series connected set of electro-magnetic coils 29a; and the contact I45-2a is connected by a conductor I45a. with the other terminal I4'I-2a of the series connected coils of the set of electro-magnets 29a.

Similarly the outer ends of the arms I4IIb and I4 I2b are arranged for movement into electrical connections respectively with contacts I45-I b and I 352b-, and by reason of the angling of the arms I4I-Ia and I4I2awith respect to the arms I4I-Ib and I4I2b, when the arms I4I-Ib and I4I--2b are in connection with the contacts I45--Ib and I452b, as illustrated in Fig. 16, the arms I4IIa and NIL-2a. are displaced out of connection with the contacts I45Ia and I45-2a.

The contact I45Ib is connected by a conductor I46-Ib' with one terminal I4'I-Ib of the series connected set of electro-magnetic coils 29b; and the contact I452b is connected by a conductor I462b with the other terminal NIL-2b of the series connected coils of the set of electromagnets 2912.

Accordingly, when the arms I4I-Ib and I4I2b are in connection with the contacts I45--Ib and I452b, as illustrated in Fig. 16, the power conductors I40--! and I402 of the power line I40 are connected with the series connected coils of the set of electro-magnets 29b and energize the same, and the circuit is broken between the power conductors and the coils of the other set of electro-magnets 29a.

Conversely, when the conductor bars are swung so that the arms I4I-Ir and I4I-2a connect with the contacts I45Ia and I45-2a, the coils of magnets 29a are energized by connection with the power line I40, and the circuit is broken between the power line M0 and the coils of the set of magnets 29b.

The preferably electro-magnetic means indicated generally by I4 Ia. and Hill) are provided for successively actuating the selector switch I4I to successively connect the power line I40 with the coils of the sets of the electro-magnets 20a and 29b.

The actuating means I4Ia includes a longitudinally movable armature I50a which is located within a solenoid coil IBM, and one end of the armature I50a is pivotally connected with one end of a non-conducting link I50a', and the other end of the link I50a' is pivotally connected with the arm I4I-2a, whereby longitudinal movement of the armature I50a towards the frame 2, as illustrated diagrammatically in Fig. 16, will swing the arms I4l-Ia and I4I-2a Cal into connection with the contacts l45-la and I45-2a when the solenoid coil I5Im is energized.

One terminal I52Ia of the solenoid; coil I5Ia is connected by a conductor I 53-Ia with the power line conductor I40I. The other terminal l522a of the solenoid coil I5Ia is connected by a conductor I53la with one contact blade EEG-Ia of a push button switch I5 la, which is mounted at one side of the outer end 44 of the swinging arm 35, as best shown in Figs. 1, 2, 4, 5, and 12 to 15 inclusive.

The other contact blade I52a of the push button switch l54a is connected by a conductor I53-2a with the power line conductor Mli--2.

The push button switch I540 includes the spaced contact blades i54la and l542a. which are preferably mounted within an insulating case I55a, and a push button I560. is slidably mounted and extends through the front wall IE'ia of the case I55a.

The inner end of the push button IBfia within the case I55a has secured thereon a contact plate I58a adapted for bridging and connecting the contact blades I5i-la and i54-2a, and the contact plate l58a is normally maintained out of connection with the blades, as by means of a compression spring I59a.

Similarly, the actuating means 1 4| b includes a longitudinally movable armature I581) which is located within a solenoid coil I5Ib, and one end of the armature I551) is preferably connected with one end of a non-conducting link I501), and the other end of the link 15% is pivotally connected with the arm Iii-2b, whereby longitudinal movement of the armature I501) towards the frame 2 will bring the armature to the position illustrated in Fig. 16, wherein the arms E4IIb and I4i2b have been swung into connection with the contacts I l5Ib and M5-2b, the solenoid coil I 5th having been energized.

One terminal I52-Ib of the solenoid coil I5Ib is connected by a conductor I53-2b' with the power line conductor 1 38-2. The other terminal I522b of the solenoid coil I5Ib is connected by a conductor I53--2b' with one contact blade i'5 i2b of a push button switch i541) which is mounted at the side of the outer end 4d of the swinging arm 45, opposite to that side on which the switch I5ia is mounted, as best shown in Figs. 2, 4, 5, and 12 to 15 inclusive.

The other contact blade Hid-II) of the switch I541) is connected by a conductor ISit-Ib with the power line conductor Mil-4.

The push button switch I 54b includes the spaced contact blades Hi l-4b and IEi4-2b which are preferably mounted within an insulating case I551), and a push button I5iib is slidably mounted and extends through the front wall Iti'ib of the case l55b.

The inner end of the push button 5556b within the case i 55b has secured thereon a contact plate I581) adapted for bridging and connecting the contact blades iEfi-lb and ISL-2b, and the contact plate I 58b is normally maintained out of connection with the blades, as by means of a compression spring I591).

The improved machine l operates as follows:

The direction of rotation of the shaft of the drive motor i"? is such that when the coils of the set of electro-magnets 29b are connected with the power line 549, as illustrated in Fig. 16, the parts of the reversing gearing I8 are positioned so that the third intermediate shaft 32 is rotating in the direction to move the swinging arm 45 in the direction of the arrow Q, that is to say, towards the cutter 8b.

In Figs. 1, 2, 3, 4, and 6 the parts of the machine are illustrated in their relative positions just after the operator has loaded the block B in the jack l0 while the arm is swinging towards the cutter 81).

It is assumed that the machine has just been started, in which event the push button I551? hasbeen instantaneously depressed by the operator to energize the solenoid coil I5ib so that the armature l5fib will be moved to swing the arms MI-Ib and Iii-2b into connection with the contacts MES-lb and I i5-2b as illustrated in Fig. 16.

From the position illustrated in Figs. 1, 2, 3, 4, and 6, the arm &5 swings to the position illustrated in Fig. 12, and during which swinging the jack Ii] has been rotated about the axis Y so that the cutter 81) cuts into one side of the block B as illustrated in Fig. 12, at exactly the desired locus with respect to the axis X.

By the time the arm 55 has reached the position illustrated in Fig. 12, the cam guide wheel I331) stops further swinging of the arm 45 by contact of the adjacent side of the outer periphery I34 of the contour cam I 30 against the cam guide wheel limb.

During swinging of the arm 55 towards the cutter 8b, as aforesaid, the vertical plane T including the high points 19 and of the tilting cam 11 and the elevating cam 83, respectively, is maintained at right angles with the vertical plane U extending through the axes of the cutters 8a and 8b, by the above described operation of the epicyclic gear train cam positioning means IIii, best shown in Fig. 11.

Also, during the swinging of the arm 45 towards the cutter 8b, the jack I 0 supported as aforesaid on the upper end of the jack elevating'and rotating shaft 39 may be differentially rotated with respect to the tilting and elevating cams 77 and 83 by reason of the fact that the epicyclic gear train jack rotating means I2 may provide a difierent speed of rotation for the jack; shaft 39 than that of the cam rotating and mounting sleeve EN.

The relative speeds of rotation of the jack elevating and rotating shaft 39 and the cam rotating and mounting sleeve BI is determined so to bring each cutter into contact with one side of the block B, at the desired locus with respect to the axes X andY.

When the arm 45 has reached the position shown in Fig. 12, the resisting torque against further swinging of the arm 45 caused by abutment of the periphery it! of the contour cam I36 against the guide wheel I381) is greater than the frictional swinging torque applied through the clutch means 54.

Accordingly, the arm 45 will swing no further towards the cutter 81), but the third intermediate shaft 32 continues its rotation, and causes rotation of the jack drive sleeve 48 and the jack rotating shaft 39 carried therein, so that the jack is rotated about the axis Y to the position shown in Fig. 13, during which rotation thefirst side of the heel block B is formed as illustrated in Fig. 13, by the cutting action of the cutter 8b, during the simultaneous rotation, tilting and elevating of the heel block, as aforesaid.

In Fig. 16 the jack parts are illustrated in the positions of Fig. 13 just before the'end of rotation of the jack in the direction of the arrow R. Fun ther rotation of the jack in the direction of the arrow R in Fig. 16 impinges one side of a push button actuating tongue I60 secured on the link bar 68 against the outer end of the push button I56a, whereby the contact plate l58a bridges across and connects the contact blades l54la, and l542a, thereby energizing the solenoid coil 15m, so that the selector switch is operated to energize the coils of the electr c-magnet set 29a. and the coils of the electro-magnet set 2531) are disconnected from the power line M8 and deenergized, consequently the reversing gearing I8 is operated to reverse the direction of rotation of the third intermediate shaft 32, whereby the arm 45 is swung away from the cutter 81) towards the cutter 8a.

The operation of the machine during cutting by the cutter 8a is the reverse of its operation during cutting by the cutter 8b.

In Fig. 14 the relative positions of the parts of the machine are illustrated at the beginning of the second cutting operation for the other side of the block B, and in Fig. 15 the relative positions of the parts of the machine are illustrated at the end of the second or final cutting operation.

In Fig. 15 the push button switch 15% is just about to be actuated by abutment of the tongue I60 against the outer end of the push button l56b to close the circuit through the solenoid coil I501), and thus open the circuit through the coils of the magnet set 29a and close the circuit through the coils of the magnet set 2%, after which the arm 45 then swings from the cutter 8a towards the cutter 8b, and during such swinging the finished heel is removed from the jack and a new block B inserted, as aforesaid.

In Fig. 17, four of the machines I are mounted on a base 200, and a single operator may move from one machine to the other unloading finished heels and loading blocks, and each of the machines may be arranged for forming a different style of heel.

The base 20 on which the plurality of the machines are mounted may be arranged for rotation about a verticalaxis manually or mechanically so that the operator need not change his position to feed the machines.

I claim:

1. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a block including a movable block positioning member, means for moving the block mounting means from one cutter to another, second means for moving the block positioning member with respect to the first moving means and with each cutter during each cutting operation, and means controlled by operation of the second moving means for operating the first moving means to move the block mounting means from one cutter to another.

2. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a block including a movable block positioning member, means for moving the block mounting means from one cutter to another, means for rotating the block positioning member with respect to the moving means and with each cutter during each cutting operation, and means controlled by operation of the rotating means for operating the moving means to move the block mounting means from one cutter to another.

3. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a block including a movable block positioning member, means for moving the block mounting means from one cutter to another, second means for moving the block positioning member with respect to the first moving means and with each cutter during each cutting operation, means for tilting the block positioning member during each cutting operation, and means controlled by operation of the second moving means for operating the first moving means to move the block mounting means from one cutter to another.

4. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a block including a movable block positioning member, means for moving the block mounting means from one cutter to another, means for rotating the block positioning member with respect to the moving means and with each cutter during each cutting operation, means for tilting the block positioning member during each cutting operation, and means controlled by operation of the rotating means for operating the moving means to move the block mounting means from one cutter to another.

5. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a block including a movable block positioning member, means for moving the block mounting means from one cutter to another, second means mounted on the first moving means and operative for moving the block positioning member with respect to the first moving means and with each cutter during each cutting operation, and means controlled by operation of the second moving means for operating the first moving means to move the block mounting means from one cutter to another.

6. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a block including a movable block positioning member, means for moving the block mounting means from one cutter to another, means mounted on the moving means and operative for rotating the block positioning member with respect to the moving means and with each cutter during each cutting operation, and means controlled by operation of the rotating means for operating the moving means to move the block mounting means from one cutter to another.

'7. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a block including a movable block positioning member, means for moving the block mounting means from one cutter to another, second means mounted on the first moving means and operative for moving the block with respect to the first moving means and with each cutter during each cutting operation, means mounted on the first moving means and operative for tilting the block positioning member during each cutting operation, and means controlled by operation of the second moving means for operating the first moving means to move the block mounting means from one cutter to another.

8. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a plurality of spaced cutters, means for mounting a. block including a movable block positioning member, means for moving the block mounting means from one cutter to another, means mounted on the moving means and operative for rotating the block positioning member with respect to the moving means and with each cutter during each cutting operation, means mounted on the moving means and operative fortilting the block positioning member during each cutting operation, and means controlled by operation of the rotating means for operating the moving means to move the mounting means from one cutter to another.

9. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including a pair of spaced cutters, a movable supporting member, means carried by the supporting member for mounting a block and including a movable block positioning member, means operatively associated with the supporting member for imparting oscillatory movement thereto back and forth between the cutters, and means for alternately guiding and rotating the block positioning member with respect to the supporting member, said structure providing means whereby one portion of the block traverses one cutter and another portion thereof traverses the other cutter so that each cutter forms a portion of a side and rear heel surface on a block secured in the mounting means.

10. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including two spaced cutters, a movable supporting member, means carried by the supporting member for mounting a block and including a movable block positioning member, means for oscillating the supporting member back and forth between the cutters, and means operatively associated with the moving means for alternately guiding and rotating the block positioning member with respect to the supporting member, said structure providing means whereby one portion of the block traverses one cutter and another portion thereof traverses the other cutter so that each cutter forms a portion of a side and rear heel surface on a block secured in the mounting means.

11. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including two spaced cutters, a movable supporting member, means carried by the supporting member for mounting a block and including a movable block positioning member, means for oscillating the supporting member back and forth between the cutters, means operatively associated with the moving means for alternately guiding and rotating the block positioning member with respect to the supporting member, said structure providing means whereby one portion of the block traverses one cutter and another portion thereof traverses the other cutter so that each cutter forms a portion of a side and rear heel surface on the block secured in the mounting means, means for moving the block positioning member longitudinally with respect to its axis of rotation, and means for tilting the block positioning member with respect to its axis of rotation.

12. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including two spaced cutters, means for mounting a block including a movable block positioning member, swinging arm means carrying the block mounting means, means for imparting oscillatory movement of the swinging arm means and block mounting means back and forth between the cutters, and means for guiding and rotating the block positioning member with respect to the swinging arm means, said structure providing means whereby one portion of the block traverses one cutter and another portion thereof traverses the other cutter so that each cutter forms a portion of a side and rear heel surface on a block secured in the mounting means.

13. Apparatus for forming curved surfaces on heel blocks and the like, the apparatus including two spaced cutters, means for mounting a block including a movable block positioning member, swinging arm means carrying the block mounting means, means for imparting oscillatory movement of the swinging arm means and. block mounting means back and forth between the cutters, means for guiding and rotating the block positioning member with respect to the swinging arm means, said structure providing means whereby one portion of the block traverses one cutter and another portion thereof traverses the other cutter so that each cutter forms a portion of a side and rear heel surface on the block secured in the mounting means, means for moving the block positioning member longitudinally BRUNO T. GIALDINI. 

